JPH0748015A - Conveyor roll - Google Patents

Abstract

PURPOSE: To provide a conveyor roll which is capable of surely holding an end cap of the conveyor roll at an end part of a roller member both in the circumferential direction and in the axial direction irrespective of large difference in thermal expansion, inexpensive in manufacture, stable in performance and provided with a durable holder. CONSTITUTION: A conveyor roller 1 includes a quartz glass roller having cylindrical end parts 11a, 11b, a pair of end caps 18a, 18b to rotatably fit the roller, and a spring holder 36 to rotatably fit each end cap to the roller. Each spring holder 36 includes a coil spring formed of a spiral coil which is flat in side part and spirally wound around the cylindrical end parts 11a, 11b of the roller, and each coil includes a bent portion and a straight portion to bring a tubular wall 20 and the cylindrical end parts 11a, 11b into elastic friction engagement with each other even when the difference in thermal expansion is generated between the tubular wall of the end caps 18a, 18b and the cylindrical end parts 11a, 11b of the roller. Each end cap includes a screw which is engaged with the coil of the holding screw and fixed to each cylindrical roller end in the axial direction on its open end.

Description

Detailed Description of the Invention

[0001]

FIELD OF THE INVENTION This invention relates generally to conveyor rolls and more particularly to the use of flat sided coil spring retainers for non-rotatably mounting end caps to ceramic roller members.

[0002]

2. Description of the Related Art In a glass plate quenching apparatus, a conveyor mechanism having a plurality of elongated ceramic rolls is used to move a glass plate in and out of a heating chamber of a furnace. The rolls are generally formed of fused silica, the ends of which are non-rotatably driven and supported by a conveyor mechanism. A pair of metal end caps are non-rotatably attached to each end of the roller member for transmitting drive torque from the conveyor mechanism to the ceramic roll. In one form of conveyor mechanism, each metal end cap includes a minor axis that is concentrically aligned with the axis of rotation of each end cap. The short axis of the end cap is rotatably received in a V-shaped member that is interposed at the upper ends of a pair of opposite support arms of the conveyor mechanism. A drive belt under one or both of the end caps on both sides applies a drive torque to the roller member, allowing the roller member to roll and transport a sheet of heated glass. In other types of conveyor systems, there is no minor axis in the end cap, which can be driven by a gear train or chain.

However, regardless of the type of conveyor system in which the conveyor rolls operate in combination, each of the metal end caps is non-rotatably attached to each end of the roller member to generate the torque generated by the drive members of the conveyor mechanism. Must be effectively transferred to the ceramic roller. Any slippage between the end cap and the end of the ceramic roller member will severely impair the operation of the conveyor roll that carries the glass sheet. Accordingly, there is a long felt need for a simple, economical and effective means for non-rotatably mounting a metal end cap for torque transmission to the end of a ceramic roller member used in a conveyor roll. It has been.

Unfortunately, the thermal environment in which the conveyor roll must operate in combination with the thermal and mechanical properties of the materials used in the roll is truly satisfactory between the end cap and the roller member. It has hampered the development of some means of retention. When a roll as described above is subjected to operating temperatures associated with glass plate quenchers (ie temperatures between 500 and 1000 ° C.), the end caps can reach temperatures near 500 ° C. or higher. The thermal expansion induced at the metal end caps at such temperatures is much greater than the amount of expansion induced at the cylindrical ends of the roller members located within the aforementioned end caps. As a result, if the end cap is simply friction fitted to the cylindrical end of the roller member, significant mechanical loosening occurs between the end cap and the end of the roller member. If such loosening becomes severe, the roller becomes a "dead roll",
As the heated glass is pushed along the conveyor mechanism by the drive applied by the other driven rolls, it can scrape and damage its tough surface. While mechanically simply connecting the end cap to the roller mechanically with screws, clamps, pins, or other conventional fasteners, the retention problem appears to be solved at first glance, but mechanical fasteners such as those mentioned above are not This is disadvantageous because it is difficult to fit the holes, screws, or other indentations in the brittle silica roller member along with the local stresses applied to the roller.

Therefore, a number of alternative methods have been attempted in the prior art for effectively connecting the end cap to the roller in a manner that eliminates the occurrence of crack-inducing stresses at the end of the roller. In one such method, a heat resistant silicone-based adhesive is applied between the cylindrical outer surface of the roller end and the inner surface of the tubular wall of the end cap. Unfortunately, silicon-based adhesives break over time and need to be replaced periodically in conveyor rolls such as those mentioned above. As a more promising method, between the end cap and the end of the roller member,
It was to use a spring-like member that continuously provided a friction holding force between these two elements. Such a method utilizes a plurality of adjacent leaf spring members, McMaster US Pat. No. 4,404,
011 and pages using circumferentially expandable and radially compressible split metal rings (Pag
e) in U.S. Pat. No. 4,399,598.

While both of the above methods appear to be an improvement over the use of currently known silicone-based adhesives, both methods are not without drawbacks. For example, in any of the retention methods disclosed in either Macmaster U.S. Pat. No. 4,404,011 or Page U.S. Pat. No. 4,399,598, the end caps are axially spaced from the end of each roller member. It does not provide a means to reliably prevent slippage. This can result in "dead rolls" rubbing the surface of the softened glass as the end caps slide axially from the rollers during operation, or the rolls rotate eccentrically, which is undesirable for glass thickness. This is important because it causes fluctuations that cause general distortion. In addition, U.S. Pat. No. 4,399, page
The split metal ring utilized as a retaining element in US Pat. No. 598 is sized in a corrugated split ring such that under ambient temperature conditions, the assembly end cap produces a very strong wedge force as it slides over each roller. Otherwise, thermal expansion of the end cap does not appear to exert a strong holding force between the roller member and the inner surface of the end cap tubular wall. When the roll is heated during use, the radial compressive force will probably relax, but during assembly, a large amount of radial compressive force will add local strain to the end of the roller, which is very small. It may cause severe cracks or other damage. Further, in order to attach the roller member to the end cap having the split ring inside, it is necessary to press the end cap into the roller in the axial direction,
Therefore, the brittle material forming the roller may be further strained. Finally, page US Patent No. 4,
The relatively large air gap between the free edge of the end cap of the construction of No. 399,598 and the cylindrical body of the ceramic roller member is between the end cap in use of the roller member and the split ring and the ceramic roller member. Makes it easier for dust and debris to accumulate. Such deposits can ultimately add undesired stress to the roller ends as the end caps and metal split rings cool and contract on the roller ends when the glass furnace is shut down. Macmaster US Patent No. 4,4
The use of eight flat leaf springs, as shown in 04,011, eliminates the aforementioned disadvantages associated with the design of the end cap retainer described in page US Pat. No. 4,399,598. Retaining means are provided, but due to the fact that the side edges of the leaf springs are not mechanically connected, they allow the springs to move circumferentially during operation of the roll, so that in the tubular wall of the end cap. It may allow the roller ends to be held non-concentrically. Such non-concentric holding causes the roll to rotate eccentrically. further,
Since it is necessary to use a temporary circumferential clamp to collectively squeeze the leaf springs around the ends of the roller members before the end caps can slip on the springs, Assembly of the device is relatively difficult and cumbersome.

[0007]

Obviously, there is a need for holding means for securely fixing the end caps of a conveyor roll to the ends of their respective roller members not only circumferentially but axially. Ideally, the retaining means should ensure that the roller is retained in the end cap even with the highest level of differential thermal expansion and that it is relatively easy to assemble without applying significant mechanical stress to the roller end. Should be. Finally, it is desirable that the retaining means be relatively inexpensive to manufacture, highly stable in performance, and durable in operation.

[0008]

SUMMARY OF THE INVENTION In general, the present invention comprises a spring retainer that non-rotatably mounts an end cap to a roller to overcome all of the aforementioned drawbacks of the prior art.
Or at least an improved ceramic conveyor roll. A conveyor roll according to the present invention comprises a ceramic roller having at least one cylindrical end and a metal end cap rotatably mounting a roller member within the conveyor assembly for receiving and surrounding the cylindrical end of the roller. An end cap having a tubular wall for holding the end cap non-rotatably on the roller member, and elastically and frictionally rubbing the annular wall of the end cap and the cylindrical end of the roller member. Retaining means including a coil spring having a plurality of interconnected angular portions along the coil for interconnection with each other around the cylindrical end of the roller member. The frictional engagement is at ambient temperature and 537.8 ° C.
When exposed to a temperature between (1000 ° F.), it retains even if there is a differential thermal expansion between the end cap and the roller end.

The angular portion of the coil of spring includes a bent portion that engages the annular wall of the end cap and a straight portion that engages the cylindrical end of the roller member. In the preferred embodiment, the sides of the spring coil define a convex polygon, such as an octagon. The minimum diameter of the coil of the spring retainer is slightly smaller than the outer diameter of the cylindrical end of the roller member so that the straight and bent portions of adjacent coils are not aligned with each other, but rather staggered or offset. . Each cylindrical end of the ceramic roller member is bounded by an annular shoulder and retains the coil spring to prevent relative axial movement between the coil spring and the roller member. Further, the annular wall of the end cap terminates in a free edge and has means for axially securing the end cap to the roller member. In the preferred embodiment, the axial locking means is a screw that threadably engages the coil of the spring as the end cap rotates relative to the cylindrical end of the roller member following the assembly operation. The pitch of the threads is preferably opposite to the pitch of the coil spring, so that the coil of the spring is wound more tightly when the thread of the end cap is screwed into the coil of the spring. The inner diameter of the screw of the axial fastening means is preferably separated by 10-20 inches from the annular shoulder which the screw faces after the end cap is fully screwed into the coil spring. The tight dimensions described above allow most debris and other debris to enter the space between the annular wall and the cylindrical end and interfere with the operation of the coil spring retaining means located therebetween. Try not to.

Finally, the roller members of the conveyor roll are preferably formed from quartz glass, while the end caps are 4140 alloy or Ledloy.
It is preferably formed from machinable steel such as 300. Further, the outer diameter of each of the end caps is preferably the same as the outer diameter of the central portion of the ceramic roller.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT Referring now to FIG. 1 of the drawings in which like reference numerals designate like elements throughout the several views, a conveyor roll 1 according to the invention is particularly suitable for hot glass sheet 5 at 500-1000.degree. It is suitable for use in a conveyor mechanism 3 forming part of a quench hardening device. The largest single element of the conveyor roll 1 is a quartz glass roller member 7. The roller member 7 comprises a wide central portion 9 which, in operation, rolls the hot glass sheet 5 into and out of a quencher furnace chamber (not shown) as shown. Cylindrical end portions 11a, b are arranged at each end of the central roller portion 9. Each of the portions 11a, b is generally bobbin-shaped, including a proximal annular shoulder 13 and a distal annular shoulder 15 that define an inner end and an outer end, respectively. The proximal annular shoulder 13 leads to a flared portion 14, which integrally connects the end portions 11a, b with the end of the central roller portion 9 as shown.

The cylindrical end portions 11a, b of the roller member 7
End caps 18a and 18b are arranged on each of the above. In a preferred embodiment, each of the end caps is preferably formed from machinable steel such as Red Roy 300 or its equivalent. Each of the end caps 18a, b includes a respective cylindrical end portion 11a,
It includes a tubular wall 20 in contact with b. Tubular wall 2 on each end cap
0 includes a free edge 22 defining an open end, an end cap for receiving the respective cylindrical end portion, and an integrally formed end wall 24 at the other end, as shown. A pair of opposed holes 25 are included in the end wall 24 of each end cap 18a, b for receiving the claws of the assembly wrench. The circular end wall 24 of each end cap 18a, b includes a minor axis 26 projecting outwardly from the wall 24 as shown. The short axis 26
The axis of rotation of each of the two is aligned with the axis of rotation of each end wall 24. When the conveyor roll 1 is installed on the conveyor mechanism 3, the short shafts 26 of the end caps 18a and 18b are connected to the short shaft holding arms 28 by a V-shaped member 29 (cap 1).
8b) (only shown in relation to 8b) is rotatably received and held in. Both end caps 18a,
The short axis holding arm for b is attached to the support table 30. A drive belt 32 is provided on the support table 30 and the end caps 18 to apply a drive torque to the roller member 7.
It is located between the a and b outer surfaces 34 of the tubular wall 20.

Each of the end caps 18a, b is provided with a respective cylindrical end portion 11a, b so that the torque applied to the end caps 18a, b is effectively transmitted to the roll member 7.
It must be fixed non-rotatably. For this purpose, a flat-sided coil spring retainer 36 is provided between the cylindrical end portions 11a, b and the inner surface 38 of the tubular wall 20 of each end cap 18a, b.

Referring to FIGS. 2, 3 and 4, the coil spring retainer 36 having flat sides is formed from a plurality of coils 40, preferably octagons, although other polygons may be used. ing. Each coil has a diameter of 0.787-0.81
It may be formed from 3 millimeters (0.031 to 0.032 inches) of ASTM grade A228 piano wire, but it is more preferred that these coils be made from a heat resistant alloy such as Inconel. Each coil 40
Bending portion 4 as best shown in FIGS. 2 and 3.
4 formed of straight portions 42 of wires that are integrally connected to each other. Referring to FIG. 3, the coil 4
The minimum inner diameter D1 of 0 is the outer diameter D of each cylindrical end portion 11a, b.
Slightly less than 2. With such a dimension, when the coil 40 of the spring retainer 36 is wrapped around each cylindrical end portion 11a, b, the frictional contact between the straight portion 42 and the bent portion 44 will be cylindrical. Parts 11a, b
Instead of being distributed linearly parallel to the axis of rotation of the, the distribution is even around these parts as best shown in FIGS. 4 and 5,
When the octagonal spring retainer 36 is in its relaxed state as shown in FIG. 2, the bends of adjacent coils 40 do not align linearly, but rather the inner circumference of each coil 40 is bounded by it. It should be noted that the shape is slightly smaller than the outer peripheries of the cylindrical end portions 11a and 11b, so that the cylindrical end portions 11a and 11b slightly move in the spiral direction. Both straight portion 42 (tangentially engaging the outer surface of cylindrical end portion 11a, b) and bent portion 44 (engaging the inner surface of tubular wall 20 of each end cap 18a, b) are as previously described. The end caps 18 may be unevenly distributed over the
Not only does it provide a firmer holding force between a, b and the respective cylindrical end portion 11a, b, but is also superior because the holding force is distributed more evenly around the end portion 11a, b. It is believed to provide concentricity.

Referring now to FIGS. 4, 6 and 7, the free edge 22 of the tubular wall 20 of each end cap 18a, b.
An annular ridge 47 is provided around its interior. Immediately in front of the annular ridge is a conical wall portion 48. Around the raised portion 47, the pitch is the spring retainer 36.
A screw 49 is provided which is twice the pitch of the spirally arranged coils and is the opposite. Spring holder 3
If the coil 40 of 6 is right-handed, the threads of the annular ridge 47 should be left-handed with the same pitch. The inner diameter of the screw 49 and the outer diameter of the proximal annular shoulder 13 are spaced apart from each other by about 10 to 20 thousandths of one inch. Such proximity results in tubular wall 20 and cylindrical end portions 11a, b.
Prevents most debris and debris from accumulating in the annular space between and. When the roll 1 is actuated, the taper of the conical wall portion 48 acts in conjunction with the separation, and accelerates and centrifuge the dust that tends to collect there. Although close spacing is possible, the Applicant has found that very fine particles of debris are
It has been discovered that it can become compacted in the thin annular space created between the inner diameter of 9 and the outer diameter of the proximal annular shoulder 13. Due to such hardening, the end caps 18a, 18b
The cooling and shrinkage of the can cause a large compressive stress in this area of the roll 1.

Returning to the description of the assembly and operation of the conveyor roll 1 with reference to FIGS. 4, 5 and 6, the end caps 18a, b first attach the coil 40 of the octagonal spring retainer 36 to the end portion 11a. , B and are attached to their respective cylindrical end portions 11a, b. The length of the coil spring retainer 36 is such that the spring retainer 36 covers substantially all of its respective cylindrical end portion such that the end portion of the spring retainer 36 is wrapped around the end portion 11a, b of the coil spring. It is preferably dimensioned so that it is immediately adjacent to the proximal and distal annular shoulders 13, 15 after completion. Coil 40
The inner circumference of is slightly smaller than the length of the outer circumference of the cylindrical end portions 11a, b, so that the straight and bent portions 42 and 44 of adjacent coils 40, in contrast to the linearly aligned shape shown in FIG. It takes the displaced position shown in FIG.

In the next stage of assembly of roll 1,
The distal end of the cylindrical end portion 11a passes through the open end defined by the free edge 22 until the screw 49 circumferentially engages the distal end of the coil spring retainer 36 through the end cap 18.
It is inserted through the open ends of a and b. Such engagement and alignment is facilitated by the conical wall 48. The end caps 18a, b are then screwed into their respective cylindrical end portions 11a, b by inserting the claws of a wrench (not shown) into the holes 25 in the end caps. In practice, Applicants have taken about 2.72-10.87 meters-kilo (20-8) to screw the end caps 18a, b into the position shown in FIG.
I found that I needed a torque of 0 foot-pounds. However, even if such a torque is applied to the roller member 7 made of ceramic, the roller member 7 is not broken without breaking.
There is no risk of breakage for the roller member 7 that is typically capable of withstanding torques of 6 ft / kg (400 ft / lbs) or more. Since the screw pitches of the screw 49 and the coil 40 of the spring retainer 46 are opposite to each other,
The act of screwing the end caps 18a, b into the position shown in FIG. 6 actually acts to tighten the coil of the spring retainer 36 around the outer surface of the cylindrical end portions 11a, b, thus increasing the holding force. In addition, the threaded engagement between the coil 40 of the spring retainer 36 and the screw 49 causes the annular shoulder 1
End caps 18a in combination with the presence of 3, 15
B is axially fixed to the end portions 11a, 11b.

As a result of the screwing operation, the spring holder 36
The straight portion 42 and the bent portion 44 of each coil 40 in FIG.
The position shown in FIG. 2 is applied to provide a holding force for non-rotatably attaching the cylindrical end portions 11a and 11b to the end caps 18a and 18b. Specifically, the central portion of each of the straight portions 42 tangentially engages the outer surface of the cylindrical end portion 11a, b and the bent portion 44 engages the inner surface 38 of the tubular wall 20 of the end cap 18a, b. In response to the radial compressive force that the screw 49 exerts on the coil 40 of the spring retainer 36, the straight portion 42 does not remain perfectly straight, but rather faces the cylindrical ends 11a, b as shown. It will bend slightly. Such bending of the straight portion 42 causes the central portion of each of the bending portions 44 to be securely engaged with the cylindrical end portions 11a, b, and further allows the bending portion 44 of the coil 40 to engage the inner surface 38 of the tubular wall 20. Generate a radial compressive force in two directions that compressively engages. The Applicant has determined that the inner diameter of the screw 49 and the outer diameter of the screw defined by the coil 40 is about 3.123-6.116 meters-kilometer (mm) to screw the end caps 18a, b into the position shown in FIG. A torque of 23 to 45 ft.-pounds) is required, and about 2% between the end caps 18a, b and the respective cylindrical end portions 11a, b are required to generate any relative rotational movement between these two elements. 0.718 to 9.513 meters / km (20 to 70
It has been found that it requires a relative torque of (ft-pound). Such holding power is usually about 1.359 to 2.03.
Sufficient torque for roll 1 operation is required as torque less than 9 meters-kilometer (10-15 ft-lb) is required to be transmitted through the end caps 18a, b.

Applicants have found that when the end caps 18a, b are exposed to high temperatures up to 600 ° C., the resulting thermal expansion causes the coil 40 of the spring retainer to end caps 18a, b and the cylindrical end 11a. , B, which is advantageously considered to increase, or at least remain the same, the holding force mentioned above. As mentioned above, under such high temperature conditions, the end cap is made of metal and the end of the roller is made of quartz so that the end cap tubular wall 2
0 expands more radially than the cylindrical ends 11a, b of the roller member 7. However, applying heat to the coil 40 of the spring retainer 36 not only increases the diameter of the wire that forms the coil, but also that the length of the straight portion 42 is less than the diameter of the wire that is used to form the coil 40. Since it is much larger, the length of the straight portion 40 of the coil 40 is further extended. The net effect of thermal expansion of the coil 40 in these two directions is that these coils cause the radial air gap between the inner surface 38 of the tubular wall 20 and the outer surface of the cylindrical end portions 11a, b to increase with temperature. Ensure that the applied holding force stays at least the same.

While the present invention has been described with reference to the preferred embodiment, many modifications, additions and variations will be apparent to those skilled in the art. Such additions, changes and modifications fall within the scope of the invention, which is defined only by the claims.

[Brief description of drawings]

FIG. 1 is a side view of a conveyor roll according to the present invention in its activated condition installed in a conveyor mechanism of a glass quenching apparatus, with both end caps and spring retainers shown in cross section for clarity.

FIG. 2 is a side view of an octagonal spring retainer with flat sides used to mechanically connect the tubular wall of each of the end caps to the cylindrical end of the ceramic roller member.

FIG. 3 is an end view of the spring holder shown in FIG. 2 taken along line 3-3.

FIG. 4 is an enlarged partial side sectional view of the conveyor roll of the present invention showing how the octagonal spring retainer interengages the cylindrical end of the ceramic roller member and the inner surface of the tubular wall of the end cap. .

5 is a line 5-5 at the end of the conveyor roll shown in FIG.
Sectional view seen along.

FIG. 6 shows the threads on the annular ridge around the free end of the tubular wall of the end cap.

FIG. 7 is a diagram showing a state of a portion surrounded by a dotted circle in FIG. 4 before a thread is cut on the annular ridge.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Conveyor roll 3 Conveyor mechanism 7 Roller member 11a, b Cylindrical end part 13,15 Annular shoulder 18a, b End cap 20 Tubular wall 22 Free edge 36 Spring retainer 40 Coil 42 Straight part 44 Bending part 49 Screw

Claims (26)

[Claims] 1. A conveyor roll for carrying objects at high temperatures, comprising a ceramic roller member having at least one cylindrical end and a metal end cap for rotatably mounting the roller member within a conveyor assembly. An end cap having a tubular wall that receives and surrounds the cylindrical end of the roller member, and retaining means for non-rotatably attaching the end cap to the roller member, the cylindrical end of the roller member Spirally wrapped around the end cap and the cylindrical end of the roller member even if there is a difference in thermal expansion between the end cap and the roller member between ambient temperature and high temperature. Retaining means including a coil spring having a plurality of interconnected angular portions along its coil for resilient and frictional engagement. Conveyor roll. 2. The coil of claim 1, wherein the coil includes a bent portion that engages a tubular wall of the end cap and a straight portion that engages a cylindrical end of a roller member. Conveyor roll. 3. The conveyor roll of claim 2, wherein the sides of the coil of the spring define a convex octagon formed from interconnected straight portions of the spring. 4. The coil of the spring is octagonal, with the apex of the octagonal coil engaging the tubular wall of the end cap and the straight side of the octagonal coil engaging the cylindrical end. The conveyor roll according to claim 2. 5. The conveyor roll according to claim 1, wherein the roller member is made of quartz glass, and the end cap is made of low carbon steel. 6. The cylindrical end is bounded by an annular shoulder that prevents relative movement between the coil spring and the cylindrical end along the axis of rotation of the cylindrical end. The conveyor roll according to claim 1, wherein: 7. The conveyor roll according to claim 1, wherein the coil spring is made of a refractory metal. 8. A conveyor roll according to claim 1, wherein the tubular wall of the end cap includes a free edge having means for axially securing the end cap to the cylindrical end of the roller member. . 9. The axial securing means is a screw that threadably engages a coil of the spring when the end cap rotates relative to the cylindrical end of the roller member. Conveyor roll described in. 10. The coil of the spring is twisted about the cylindrical end when the screw engages the coil because the pitch of the screw of the axial fixing means is opposite to the pitch of the coil spring. The conveyor roll according to claim 9, wherein the conveyor roll is wound tightly. 11. A conveyor roll for carrying heated objects along a conveyor assembly, comprising ceramic roller members having cylindrical ends on opposite sides, and rotatably mounting the ceramic roller members within the conveyor assembly. A pair of metal end caps each having a tubular wall that receives and surrounds one of the cylindrical ends of the roller member; and each of the end caps is non-rotatable with respect to the roller member. A pair of retaining means for attaching to each of the retaining means including a coil spring helically wound around the cylindrical end of the roller member, each coil of the spring being exposed to ambient and high temperatures. Elastically frictionally interengage the tubular wall of the end cap with the cylindrical end of the roller member, even if there is a difference in thermal expansion between the end cap and the roller member. Holding means including angular portions connected to each other. 12. A straight portion of the coil, wherein sides of the coil of the spring define a convex polygon, the straight portions of which are all of the same length and which intersect adjacent straight portions at approximately the same angle. 12. The conveyor roll of claim 11, wherein the bends are defined by the intersections of. 13. The conveyor roll according to claim 11, wherein the ceramic roller member is made of quartz glass, and the end cap is made of machinable steel. 14. The inner diameter of the coil spring is smaller than the outer diameter of the cylindrical end of the roller member, so that the inner diameter of the coil of the spring frictionally grips the outer surface of the cylindrical end, and 13. A conveyor roll according to claim 12, wherein the intersections of the portions are distributed around all points around the cylindrical end. 15. The coil of the spring is octagonal, the apex of the octagonal coil engaging the tubular wall of the end cap, and the straight side of the octagonal coil engaging the cylindrical end. The conveyor roll according to claim 11, wherein the conveyor roll is a roll. 16. The cylindrical end is bounded by an annular shoulder that blocks relative movement between the coil spring and the cylindrical end along the axis of rotation of the cylindrical end. The conveyor roll according to claim 11, wherein the conveyor roll is a roll. 17. The end cap tubular wall is free of axial locking means including screws that threadly engage the coil of the spring to axially lock the end cap to the cylindrical end. The conveyor roll of claim 11, including an edge. 18. The pitch of the screw of the axial locking means and the pitch of the coil of the spring so that the coil of screw is more tightly wound around the cylindrical end when the screw engages the coil. 18. The conveyor roll of claim 17, wherein the rolls are opposite to each other. 19. A distal and proximal annulus for the cylindrical end to prevent relative movement between the coil spring and the cylindrical end along the axis of rotation of the cylindrical end. A conveyor roll according to claim 17, characterized in that it is bounded by shoulders. 20. The screw has an inner diameter of 10/1000.
20 inches closely spaced about the outer diameter of the proximal annular shoulder to prevent debris and debris from entering the space between the annular wall of the end cap and the cylindrical end of the roller. 20. The conveyor roll according to claim 19, wherein: 21. A conveyor roll for carrying heated glass sheets along a conveyor assembly, comprising: a quartz glass roller member having cylindrical ends on both sides; made of a heat resistant alloy; A pair of end caps for rotatably mounting a roller member, each end cap receiving and surrounding one of the cylindrical ends of the roller member; and each of the end caps being non-rotatable to the roller member. Retaining means for mounting, including a flat sided coil spring formed from a flat sided coil spirally wound around the cylindrical end of the roller member, The spring material forming the coil develops a differential thermal expansion between the end cap and the cylindrical end when the roll is exposed to ambient temperatures and temperatures between 537.7 ° C (1000 ° F). Conveyor rolls, characterized in that it comprises a retaining means including a bent portion and a straight portion which engages resiliently, and friction and the cylindrical end portion of the tubular wall and the roller member of the end cap as the. 22. A free edge in which the tubular wall of the end cap has axial locking means including screws that threadly engage the coil of the spring to axially lock the end cap to the cylindrical end. 22. The conveyor roll of claim 21, including: 23. The pitch of the threads of the axial fastening means and the coil of the spring so that the coil of the spring is wound more tightly around the cylindrical end when the screw is threadedly engaged with the coil. 23. Conveyor roll according to claim 22, characterized in that the pitch is opposite to each other. 24. The cylindrical end is provided with distal and proximal annular shoulders that prevent relative movement between the coil spring and the cylindrical end along the axis of rotation of the cylindrical end. 24. The conveyor roll of claim 23, which is bounded. 25. The inner diameter of the screw is closely spaced about the outer diameter of the proximal annular shoulder to prevent debris and debris from entering the space between the annular wall of the end cap and the cylindrical end of the roller member. 25. The conveyor roll of claim 24, wherein the conveyor roll is blocked from entering. 26. A retainer for non-rotatably mounting a metal end cap to a cylindrical end of a ceramic roller member, the end cap having a tubular wall for receiving and surrounding the cylindrical end of the roller member. The retainer is spirally wound around the cylindrical end of the roller member to provide an end cap even if a difference in thermal expansion occurs between the end cap and the roller member between ambient temperature and high temperature. A coil spring having a plurality of interconnected angular portions along its coil for resiliently and frictionally engaging the tubular wall and the cylindrical end of the roller member with each other. Characteristic holder.